CN1904420A - Temperature-type expansion valve - Google Patents
Temperature-type expansion valve Download PDFInfo
- Publication number
- CN1904420A CN1904420A CNA2006101087065A CN200610108706A CN1904420A CN 1904420 A CN1904420 A CN 1904420A CN A2006101087065 A CNA2006101087065 A CN A2006101087065A CN 200610108706 A CN200610108706 A CN 200610108706A CN 1904420 A CN1904420 A CN 1904420A
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- valve
- valve body
- passage
- temperature
- operating stem
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
- F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/068—Expansion valves combined with a sensor
- F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7781—With separate connected fluid reactor surface
- Y10T137/7782—With manual or external control for line valve
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Temperature-Responsive Valves (AREA)
Abstract
A temperature-type expansion valve 1 includes a valve housing 110 having a first passage 121 into which a high pressure refrigerant flows, a second passage 122 through which a low pressure refrigerant flowing to an evaporator 5 flows, and a throttle passage 125 communicating the first passage 121 with the second passage 122 ; a valve body 130 having a valve member 131 varying a sectional area of the throttle passage 125 ; and an operation rod 135 for driving the valve body 130 in the interlocking arrangement with a displacement member 160 undergoing displacement in accordance with a pressure difference between a saturation pressure corresponding to an outlet temperature of the refrigerant of the evaporator 5 and an evaporation pressure of the evaporator; wherein a slide hole 124 communicating with the throttle passage 125 and accommodating the valve body 130 is formed in the valve housing 110 ; and the valve member 131 moves inside the slide hole 124 in the interlocking arrangement with the operation rod 135 to thereby adjust the sectional area of the throttle passage 125. Construction can be simplified and the number of components can be decreased.
Description
Technical field
The present invention relates to a kind of temperature-type expansion valve, this temperature-type expansion valve is installed on the air-conditioning equipment such as motorcar air conditioner, is used for supplying to according to the temperature control of refrigeration agent the flow of the refrigeration agent of vaporizer.
Background technique
For example, uncensored, publication number is this temperature-type expansion valve of describing in the Japan Patent of NO.2002-310538, comprise prismatic valve chest, first passage, be formed on the valve chamber in the first passage, second channel, throttling passage, spherical valve body, third channel and operating stem, described first passage is formed on and is used for passing through of high-pressure refrigerant in the valve chest, described second channel and first passage are formed on abreast and are used to deliver to passing through of vaporizer side refrigeration agent in the valve chest, the valve base element that is used to be communicated with valve chamber and second channel is pushed in the described throttling passage, described spherical valve body is oppositely disposed in the throttling passage, described third channel is used for passing through of the refrigeration agent of sending back to from vaporizer side, described operating stem be used for sensing by the refrigeration agent of third channel temperature and drive valve body.
Under the situation that is installed in advance between valve body and the operating stem, above-mentioned valve base element is fixed on the throttling passage.Operating stem has the small diameter portion that is inserted in the valve base element, and spherical valve body is fixed on the far-end of small diameter portion.As a result, the opening area of throttling passage can be regulated by the displacement of valve body.
Yet as flow regulating function, above-mentioned Japan Patent uncensored, that publication number is NO.2002-310538 has used complicated structure, and wherein bar-shaped operating stem, spherical valve body, tubular valve seat element etc. are consisted of one in advance.In these elements, valve base element is coupled to the small diameter portion of operating stem, but gapped because of guaranteeing between valve base element and the small diameter portion, for example, when being fixed to throttling passage on by press fit valve base element, still there is the problem that centers by the use operating stem.
In this structure, valve body and operating stem are fixed.When operating stem was soldered on the valve body, for example, because the fusion penetration of welding, changing appearred in the length of operating stem.When valve base element by using such operating stem, when being fixed on the throttling passage, show distortion at the end of operating stem by press fit, thereby descend by the validity of expansion valve control flow rate.
Summary of the invention
In view of the above problems, the object of the invention is to propose a kind of the have simple structure and the temperature-type expansion valve of member seldom.
For achieving the above object, the present invention proposes a kind of temperature-type expansion valve, described temperature-type expansion valve comprises valve chest (110), and described valve chest (110) has the refrigeration agent that high-pressure refrigerant flows to first passage (121) in it, the low pressure refrigerant that flows to vaporizer (5) flows through its second channel (122), described vaporizer (5) outlet side and flows through its third channel (123) and the throttling passage (125) that is communicated with first passage (121) and second channel (122); Valve body (130), described valve body (130) have the valve element (131) of the sectional area that changes described throttling passage (125); Operating stem (135), described operating stem (135) is used for driving described valve body (130) in linkage with displacement component (160), and the pressure difference between the saturation pressure that described displacement component (160) basis is corresponding with the outlet temperature of the refrigeration agent of vaporizer (5) and the evaporating pressure of vaporizer (5) produces (experience) displacement; Wherein be formed in the valve chest (110) with the slide opening (124) that throttling passage (125) is communicated with and holds valve body (130); And valve element (131), described valve element (131) moves in slide opening (124) in linkage with operating stem (135), thereby regulates the sectional area of throttling passage (125).
According to the present invention, valve body (130) is the slide valve system at axially reciprocating, and the result comprises that the described valve system of valve body (130), valve element (131) and slide opening (124) can be simple.Because do not need in the past essential fixing such as welding or press fit, the precision that flow control is carried out can be enhanced.
Among the present invention, slide opening (124) is the hole that direction from described valve chest (110) forms, and described slide opening (124) forms the tip engages that valve body (130) can be from the end of slide opening (124), and throttling passage (125) is at its bottom opening.
According to the present invention, can be such as the composition member of the valve system of the valve body with valve element (131) (130), operating stem (135), the spring element (133) that occurs later and first and second seal elements (136,137) that occur later from a direction assembling.Because the quantity of installation step can so be reduced, so assembly factor can be enhanced.
Among the present invention, valve body (130) has valve element (131) and guided portion (132), and described valve element (131) has bar-like shape, and described bar-like shape has minor diameter, and described guided portion (132) has the diameter greater than valve body (130).According to the present invention, valve system can constitute with simple form.More specifically, valve body (130) can be by guided portion (132) and valve element (131) form as one at least.
Therefore, valve body (130) and be used to hold the slide opening (124) of valve body (130) can be by easily forming such as welding or the machining that pushes, and valve system does not need essential in the past fixing such as welding or press fit.Therefore, the precision of flow control execution can be enhanced.
Among the present invention, be formed in the valve element (131) as the connecting port (131a, 131b, 131c) of fluid passage, and at least one and operating stem (135) in the connecting port (131a, 131b, the 131c) opening area of regulating throttling passage (125) in linkage.
According to the present invention, at least one in the described connecting port (131a, 131b, 131c) can combine with the open part of throttling passage (125).Therefore, can form valve system with simple structure.
In the valve system of the prior art of spherical valve body and tubular valve seat combination of elements,, therefore there is the problem of the autoexcitation vibration that valve body occurs on the direction of displacement of valve body therein because refrigeration agent flows.Therefore, in the present invention, the flow direction of refrigeration agent from throttling passage (125) to valve element (131) and the glide direction square crossing of valve body (130), thus be not easy to take place the autoexcitation vibration.As a result, the undesirable noise that the autoexcitation vibration causes can not appear.
Among the present invention, at least one the bottom opening in the described connecting port (131a, 131b, 131c) towards slide opening (124).According to the present invention, the refrigeration agent of decompression flows through the bottom of slide opening (124), and the low-pressure after pressure reduces affacts on the operating stem (135).As a result, the driving force that is used to drive the displacement component (160) of operating stem (135) and valve body (130) can be reduced, and the diameter of displacement component (160) is that the diameter of barrier film can be reduced.
Among the present invention, form, and peripheral groove (131d) and operating stem (135) are regulated the opening area of throttling passage (125) in linkage as the peripheral groove (131d) of fluid passage periphery around valve element (131).
According to the present invention, peripheral groove (131d) can be than easier being positioned in the throttling passage (125) in foregoing invention, and can constitute the valve system with simple structure.Desirable, with at least one combination in peripheral groove (131d) and the connecting port (131a, 131b, 131c).
Among the present invention, described throttling passage (125) has the proportional substantially sectional shape of relation between the opening area of the displacement amount that makes valve element (131) and throttling passage (125).When throttling passage (125) for example substantially during rectangular shaped, the displacement amount of opening area and valve element (131) has proportionate relationship substantially.As a result, the raising of flow control execution validity is accomplished.
Among the present invention, described valve body (130) comprises first seal element (136) that is used for the pressure difference between gas tight seal third channel (123) and the second channel (122).According to the present invention, first seal element (136) can easily be arranged on the valve body (130), and under the situation of the assembly factor that does not hinder valve body (130), can be assembled on the valve chest (110).
Among the present invention, described valve body (130) comprises second seal element (137) that is used for the pressure difference between gas tight seal first passage (121) and the second channel (122).According to the present invention, second seal element (137) can easily be arranged on the valve body (130), and under the situation of the assembly factor that does not hinder valve body (130), can be mounted in the mode identical with foregoing invention on the valve chest (110).
Among the present invention, be used for the outlet refrigeration agent that the spring element (133) of excitation (actuating) described displacement component (160) is arranged to described vaporizer (5) and have the degree of superheat, adjusting screw rod element (140) further is provided for regulating the spring force of described spring element (133), and described spring element (133) places between described valve body (130) and the described adjusting screw rod element (140).
According to the present invention, valve body (130), spring element (133) and adjusting screw rod element (140) can be contained in according to the order of appointment in the slide opening (124).As a result, valve body (130), spring element (133) and adjusting screw rod element (140) can be assembled from a direction, and can easily realize the meticulous adjusting of the degree of superheat.
Among the present invention, the outlet refrigeration agent that is used to encourage the spring element (133) of displacement component (160) to be arranged to vaporizer (5) has the degree of superheat, and spring element (5) places between valve body (130) and the slide opening (124).
According to the present invention, spring element (133) can be assembled from the direction identical with valve body (130).The size of spring element (133) also can be reduced.
Among the present invention, valve body (130) and operating stem (135) form can Regulation spring element (133) spring force.According to the present invention, the length of operating stem (135) can connect valve body (130) and operating stem (135) is conditioned by for example meshing.As a result, do not arranging the accurate adjusting that can easily realize the degree of superheat under the situation of controlling mechanism independently.
Among the present invention, described displacement component (160) has the transmission component (163) that is used for driving force is delivered to operating stem (135), and valve body (130) and operating stem (135) or comprise that the transmission component (163) of operating stem (135) forms as one.
According to the present invention, the number of member can reduce, and can improve the assembling validity that is connected length of transmission component (163), valve body (130) and operating stem (135).As a result, because the displacement amount of displacement component (160) can be delivered to valve body (130) exactly, so the validity that flow control is carried out can be enhanced.
By way of parenthesis, the label in each bracket is represented the corresponding relation of the concrete device among the embodiment who occurs later.
With reference to accompanying drawing, from the description of preferred embodiment as described below of the present invention, the present invention can more fully be understood.
Description of drawings
Among the figure:
Fig. 1 is the integrally-built schematic representation according to the temperature-type expansion valve 1 of the first embodiment of the present invention;
Fig. 2 is formed in the longitudinal cross-section view according to the position relation of the coolant channel in the valve chest 110 of the first embodiment of the present invention;
Fig. 3 A is the integrally-built longitudinal cross-section view according to the valve body 130 of the first embodiment of the present invention;
Fig. 3 B is the view of being done along Fig. 3 A center line A;
Fig. 4 A-4C be in the valve element 110 in the second embodiment of the present invention each shape and the schematic representation of throttling passage;
Fig. 5 shows the chart that concerns between the displacement amount and opening area when shape when valve element 110 and throttling passage is as parameter;
Fig. 6 is the integrally-built schematic representation of the temperature-type expansion valve 1 of a third embodiment in accordance with the invention;
Fig. 7 is the integrally-built schematic representation of the temperature-type expansion valve 1 of a fourth embodiment in accordance with the invention;
Fig. 8 is the integrally-built schematic representation of temperature-type expansion valve 1 according to a fifth embodiment of the invention;
Fig. 9 is the integrally-built schematic representation of temperature-type expansion valve 1 according to a sixth embodiment of the invention;
Figure 10 is the integrally-built schematic representation of temperature-type expansion valve 1 according to a sixth embodiment of the invention;
Figure 11 is the integrally-built schematic representation of temperature-type expansion valve 1 according to a sixth embodiment of the invention;
Figure 12 is the integrally-built schematic representation of temperature-type expansion valve 1 according to a seventh embodiment of the invention;
Figure 13 is the integrally-built schematic representation according to the temperature-type expansion valve 1 of the eighth embodiment of the present invention; And
Figure 14 is the integrally-built schematic representation of temperature-type expansion valve 1 according to still a further embodiment.
Embodiment
(first embodiment)
Hereinafter with reference to the temperature-type expansion valve of Fig. 1-3B explanation according to the first embodiment of the present invention.Fig. 1 is the integrally-built schematic representation of showing temperature formula expansion valve 1.Fig. 2 is formed in the longitudinal cross-section view of the position relation of the coolant channel in the valve chest 110.Fig. 3 A is the integrally-built longitudinal cross-section view that shows valve body 130, and Fig. 3 B is the view of being done along Fig. 3 A center line A.
As shown in fig. 1, temperature-type expansion valve 1 (only being called " expansion valve " hereinafter) with form known refrigeration cycle such as building blocks of functions such as compressor 2, condenser 3, cistern 4 and vaporizers 5, and these members connect by refrigerant tubing 6.
As shown in figs. 1 and 2, coolant channel comprises first passage 121, second channel 122, third channel 123, throttling passage 125 and communication passage 126, described first passage 121 is communicated with the outlet of cistern 4, described second channel 122 is communicated with the import of vaporizer 5, outlet in the side of described third channel 123 with vaporizer 5 be communicated with and its side in another suction side with compressor 2 be communicated with, described communication passage 126 is communicated with first and second passages 121 and 122 by the slide opening that occurs later 124.
Thereby third channel 123 forms the top that through hole runs through valve body 130.The low pressure refrigerant that is evaporated by vaporizer 5 a from then on end of through hole flows to and flows out to compressor 2 from another end.Open part 123a is formed on the last intermediate portion of this third channel 123.This open part is to be used for and will to flow through the open pore of the displacement component 160 of heat transfer above being arranged in open part 123a of the refrigeration agent of third channel 123.
More specifically, excircle and slide opening 124 that the shape of slide opening 124 forms the valve element 131 (describing below) with minor diameter connect in the bottom, and diameter connects in top greater than the excircle and the slide opening 124 of the director element 132 (describing below) of the diameter of valve element 131.The step portion 124a that is formed on slide opening 124 the insides maintains an end in spring element 133 ends.By way of parenthesis, slide opening 124 is an end openings in the circular hole at the end and the circular hole end that this has the end to be arranged and another end is not a through hole.
As a result, the refrigeration agent order according to appointment in valve chest 110 that flows to first passage 121 flows through throttling passage 125, slide opening 124, communication passage 126 and second channel 122.By way of parenthesis, label 127 expressions are used to arrange the open part of displacement component 160.Helical thread portion 127a is formed on the opening portion office and can be connected with displacement component 160 by engagement.The refrigeration agent of third channel 123 is crossed on the admittance surface of label 128 expression seal elements 167, described seal element 167 gas-tight ground sealant flow from the outside.
Secondly, displacement component 160 is the drive units that are used for driving according to displacement amount valve body 130, and described displacement amount is with changing corresponding to the pressure difference between the evaporating pressure of the saturation pressure of the outlet temperature of the refrigeration agent that flows through third channel 123 and vaporizer 5.As shown in fig. 1, displacement component 160 comprises container body 161, barrier film 162, transmission component 163 etc.Described container body 161 has loam cake 161a and lower cover 161b and is formed on helical thread portion 161c on the lower cover 161b, and each is formed described loam cake 161a and lower cover 161b by stainless steel.
On the other hand, the temperature that flows through the refrigeration agent of third channel 123 is passed to upward pressure chamber 164 by container body 161, transmission component 163 and barrier film 162.As a result, act on the barrier film 162 corresponding to the saturation pressure as the temperature of the refrigeration agent of operating liquid, described temperature is delivered to the inside of upward pressure chamber 164 by heat.
Therefore, act on the barrier film 162 in upward pressure chamber 164 corresponding to the saturation pressure of the outlet temperature of the refrigeration agent that flows through third channel 123, and the evaporating pressure of vaporizer 5 acts on the barrier film 162 in downforce chamber 165.In other words, because the pressure difference between the evaporating pressure of the saturation pressure of upward pressure chamber 164 and downforce chamber 165, barrier film 162 produces displacement, and transmission component 163 has also also produced displacement with barrier film 162 interlocks.
Secondly explain the structure of valve body 130 with reference to Fig. 1 and 3A.Valve body 130 is formed by stainless steel, is cylinder form substantially, and be received with slide opening 124 in connect.Valve body 130 can be in slide opening 124 axially reciprocating.
The valve flow passage is communicated with area based on valve body 130 change in location in the axial direction with valve body 130.In other words, when valve body was mobile in slide opening 124, the sectional area that is formed on the throttling passage 125 in the valve chest 110 can be conditioned.
More specifically, valve body 130 among this embodiment has large diameter guided portion 132 by the valve element 131 with minor diameter with in the bottom of valve body 130 as shown in Figure 3A and 3B and forms, and under the situation that spring element 133 is assembled, when the opening end from slide opening 124 was inserted into, described valve body 130 can be assembled.
The part of valve body 130 in slide opening 124 has such shape, promptly from the opening end of slide opening 124 towards closed end, outer diameter is constant or descend.The shape of the part of valve body 130 in slide opening 124 forms its diameter and diminishes gradually or progressively.This structure makes can carry out the assembling of a direction.
By way of parenthesis, connecting port 131a and 131b form in the mode identical with throttling passage 125 has identical minor diameter, and the shape of connecting port 131c forms and has bigger diameter.The shape of the peripheral groove 131d that forms around the periphery of connecting port 131a forms and can change the opening area of throttling passage 125 towards slide opening 124.
In other words, when valve body 130 moved down in slide opening 124, the opening area of throttling passage 125 increased.That is, the displacement amount that the shape of groove 131d forms valve body 130 is big more, and the opening of throttling passage 125 (valve is opened) degree becomes big more.Therefore, and when displacement amount is big, the flow that flows through the refrigeration agent of peripheral groove 131d and connecting port 131a increases.
After connecting port 131a, freezing mixture flows through connecting port 131b, connecting port 131c, communication passage 126 and second channel 122 according to the order of appointment.Because connecting port 131b opens, acted on the bottom of slide opening 124 by the refrigerant pressure of throttling passage 125 and connecting port 131a reduction.
More specifically, spring element 133 is made of helical spring, the diameter of described spiral spring is equal to or slightly less than the diameter of guided portion 132, and described spiral spring is assembled on the periphery on the valve element 131 by this way, and promptly an end in its end is arranged in the step portion 124a of slide opening 124, the upper end that another end is arranged in valve element 131.As a result, the spring force of spring element 133 can act on the displacement component 160 by operating stem 135 and promote displacement component 160.Therefore, transmission component 163 is upwards promoted by the spring force of spring element 133.
At this, explanation had the manufacture method of the expansion valve 1 of said structure.At first, as shown in Figure 2, the working angles that is formed on each coolant channel in the valve chest 110, slide opening 124, open part 123a and 127 etc. can carry out from a direction.Especially, with regard to slide opening 124, boring can be carried out from the side of upper shed part 123a and 127.
With regard to throttling passage 125 and communication passage 126, boring also can be carried out from the side of first passage 121 or second channel 122.In valve body 130, on the other hand, as shown in Fig. 3 B, each connecting port 131a-131c and peripheral groove 131d can easily form.
In the time of in valve body 130 is mounted to valve chest 110, an end in the end of operating stem 135 is coupled in the end in the end of guided portion 132 in advance.So, spring element 133 and valve body 130 can be accommodated in the slide opening 124 from a direction.
Admit on the surface 128 and during with displacement component 160 engagements, displacement component 160 can be disposed in the valve chest 110 when seal element 167 is mounted to.By way of parenthesis, for assembly displacement element 160, when one in the end of end in the end of operating stem 135 and transmission component 163 terminal engagement, engagement is achieved.According to this assembly method, valve body 130, spring element 133, operating stem 135 and displacement component 160 can be assembled from a direction.
Next will explain the operation of this embodiment's expansion valve 1.Stream passes through throttling passage 125 from the liquid refrigerant of cistern 4 from first passage 121, and when it also passed through connecting port 131a and 131b by the gap (peripheral groove 131d) between valve element 131 and the slide opening 124, described liquid refrigerant adiabatic expansion also became atomized refrigerant.Refrigeration agent flows out to vaporizer 5 by connecting port 131c, communication passage 126 and second channel 122 then.
On the other hand, the refrigeration agent that is evaporated by vaporizer 5 flows to third channel 123 and is inhaled into the suction side of compressor 2.At this, the flow that flows to the refrigeration agent of second channel 122 by peripheral groove 131d and connecting port 131a, 131b from first passage 121 determines by the extent of opening of valve element 131 by throttling passage 125, is promptly determined by valve opening.
In other words, the evaporating pressure of saturation pressure in upward pressure chamber 164 and vaporizer 4 adds that the position valve body 130 of the spring force balance of spring element 133 keeps its balance, saturation pressure described in the figure acts on by the direction of biased downward at transmission component 163, and evaporating pressure described in the figure acts on the direction that transmission component 163 is biased upwardly.
For example, when the temperature in the compartment raise and explosive vaporization occurs in vaporizer 5, the degree of superheat of vaporizer 5 raise.As a result, the saturation pressure of rising of refrigerant outlet temperature and upward pressure chamber 164 rises.As a result, transmission component 163 is pushed downwards in the drawings and valve body 130 moves down with operating stem 135, thereby increases valve opening.As a result, flow out to the flow increase of the refrigeration agent of vaporizer 5.
When the temperature in the compartment descends and during the degree of superheat step-down of vaporizer 5, transmission component 163 moves up on the contrary with aforesaid operations.Because valve body 130 moves up with operating stem 135, thereby valve opening reduces, and the flow of the refrigeration agent of flow evaporation device 5 reduces.
By way of parenthesis, because the displacement of displacement component 160, valve body 130 is allowed to to-and-fro motion in vertical direction among the figure, thereby the system that changes valve opening is commonly called " slide valve system ".According to this slide valve system, valve element 131 can advantageously generate simple structure and minor diameter.
As a result, allow the slide valve system of valve body 130, comprise that the valve system of valve body 130, valve element 131 and slide opening 124 can form simple structure at axially reciprocating because used.Because what in the past essential passing through welded or pushed for spherical valve mechanism is fixing unnecessary, the validity that flow control is carried out can be improved.
And because valve body 130 has the bar-shaped valve element 131 of minor diameter and the diameter guided portion 132 greater than the diameter of valve element 131, valve system can form simple form.More specifically, valve body 130 can be by guided portion 132 and valve element 131 are integrally formed at least.
Because valve body 130 holds the slide opening 124 of valve body 130 by can easily forming such as the machining of cutting with being used to, essential in the past such as welding with push under the unnecessary situation of the fixing means of valve system of (clamp-oning), the validity that flow control is carried out can be enhanced.
By way of parenthesis, peripheral groove 131d forms around the periphery of valve element 131, and peripheral groove 131d and operating stem 135 are regulated the opening area of throttling passage 125 in linkage.Thereby because peripheral groove 131d can combine with the open part of throttling passage 125, valve system can form simple structure.
In the valve system of the prior art of spherical valve body and tubular valve seat combination of elements,, there is the problem of the self-sustained vibration that valve body occurs on the direction of displacement of valve body because refrigeration agent flows.Therefore, in the present invention, the flow direction of refrigeration agent from throttling passage 125 to valve element 131 and the glide direction square crossing of valve body 130, thus the autoexcitation vibration is not easy to take place.As a result, the undesirable noise that the autoexcitation vibration causes can not appear.
Be formed on connecting port 131a, 131b in the valve element 131 and at least one the bottom opening among the 131c to slide opening 124.Therefore, when the refrigeration agent of decompression flow through the bottom of slide opening 124, after pressure reduced, lower pressure affacted on the operating stem 135.
As a result, the driving force that is used to drive the displacement component 160 of operating stem 135 and valve body 130 can be reduced, and the diameter of displacement component 160 is that the diameter of barrier film can be reduced.
Be placed on gap between spring element 133 and the valve body 130 because be used for the spring element 133 of bias voltage displacement component 160, spring element 133 can be assembled from the direction identical with valve body 130.The size of spring element 133 can be reduced.
(second embodiment)
In this embodiment, when the sectional shape of the peripheral groove 131d of the sectional area that is used to change throttle valve 125 or connecting port 131a changed, the relation between displacement amount and the opening area was determined.Particularly, according to the experiment that the present inventor finishes, the relation when peripheral groove 131d forms between displacement amount and the opening area is proportional substantially, and the validity of flow control can improve.
Make an explanation with reference to Fig. 4 A-4C and Fig. 5 below.Fig. 4 A-4C be show peripheral groove 131d or be formed on throttling passage 125 and valve element 131 in the schematic representation of shape of connecting port 131a.Fig. 5 shows the chart that concerns between the displacement amount and opening area when the shape shown in Fig. 4 A-4C is used as parameter.
Among Fig. 4 A, throttle valve 125 forms the circular hole with diameter of phi d.The width of peripheral groove 131d is d, and d also is the diameter of the circular hole of throttle valve 125.Among Fig. 4 B, throttling passage 125 forms the circular hole with diameter of phi d, and with the circular hole of throttling passage 125 in the same connecting port 131a be formed in the valve element 131.
Among Fig. 4 C, the width of peripheral groove 131d that throttling passage 125 forms the rectangular opening of d * π d/4 and valve element 131 is the same with d among Fig. 4 A.Compare with reference to Fig. 5 based on the displacement amount of these shapes and the relation between the opening area.
With reference to Fig. 5, the performance of the shape shown in the symbol A representative graph 4A, the performance of the shape shown in the B representative graph 4B, and the performance of the shape shown in the C representative graph 4C.Shape optimum shown in Fig. 4 C.
By the way, the performance shown in the A has proportionate relationship substantially and presents in fact enough performances in the chart.B in the chart departs from proportionate relationship, but in the case, the production of shape is easier to.Yet,, need be used to locate the assembling validity in each hole to this shape.Forming the guided portion 132 of valve body 130 for example, rectangular shape is desirable.
From above-mentioned second embodiment, can understand: navigate to throttling passage and become easier, and by form peripheral groove 131d in valve element 131, valve system can form has the structure of more simplifying.Throttling passage 125 has the proportional substantially sectional shape of the relation that makes between displacement amount and the opening area.Therefore, when throttling passage 125 for example had rectangular shape, the displacement amount of opening area and valve element 131 had proportionate relationship substantially.As a result, the raising of flow control execution validity is accomplished.
(the 3rd embodiment)
In the previous embodiment, valve body 130 forms columniform substantially shape, and slide opening 124 forms by this way, and promptly the periphery of the valve element 131 of valve body 130 and guided portion 132 connects in each other and valve body 130 is contained in the slide opening 124.Yet this structure is not restrictive.For example, also can arrange the seal element that is used for gap between gas tight seal valve body and the slide opening 124.
Particularly, as shown in Figure 6, for the pressure difference between gas tight seal third channel 123 and the second channel 122, be the refrigerant inlet of vaporizer 5 and the pressure difference between the refrigerant outlet, in the periphery of guided portion 132, form recessed groove, and be coupled in the groove such as first seal element 136 of O shape circle.
In order to seal the pressure difference between first passage 121 and the second channel 122, i.e. height difference on the refrigeration cycle, recessed groove forms around the periphery of valve element 131, and may be fitted in the groove such as second seal element 137 of O shape circle.
According to this structure, first and second seal elements 136 and 137 can easily be arranged on the valve body 130, and under the situation of the assembly factor that does not hinder valve body 130, valve chest 110 is assembled.
(the 4th embodiment)
In the foregoing description, the opening area that is connected to the throttling passage 125 of first passage 121 is regulated by the peripheral groove 131d that is formed on the valve element 131, but also can use following structure.That is, the opening area that is connected to the throttling passage 125 of second channel 122 can be regulated by the peripheral groove 131d that is formed on the valve element 131, more specifically as shown in Figure 7.
Yet in the case, communication passage 126 is formed between first passage 121 and the slide opening 124, and throttling passage 125 is formed between second channel 122 and the slide opening 124.Two connecting port 131a and 131b are formed in the valve element 131.
According to aforementioned structure, the high-pressure refrigerant that flows to first passage 121 flows to the bottom of slide opening 124, flows through connecting port 131b and connecting port 131a successively then by communication passage 126.Therefore, in the case, refrigeration agent experiences adiabatic expansion in connecting port 131b, connecting port 131a and throttling passage 125, and after its flow was conditioned in peripheral groove 131d and throttling passage 125, refrigeration agent flow through throttling passage 125 and second channel 122.
As a result, the refrigeration agent that pressure reduces and flow is conditioned flows to vaporizer 5.Yet in the bottom of slide opening 124, high pressure acts on the operating stem 135.In other words, in this embodiment, the displacement amount of displacement component 160 requires to be higher than the saturation pressure that is applied to the pressure on the operating stem 135, and the diameter of displacement component 160, and promptly the diameter of barrier film must increase.
Because pressure difference occurred this moment between the bottom of third channel and slide opening 124, preferably, the 3rd seal element 138 is set to set up hermetic seal around the periphery of valve body 130.
(the 5th embodiment)
In the previous embodiment, form the valve body 130 that has around the peripheral groove 131d of connecting port 131a periphery, but have only peripheral groove 131d to be formed on the valve element 131, and do not form connecting port 131a.
In the case, can be formed in the communication passage 126 that forms between second channel 122 and the slide opening 124 from the downward-sloping obliquely inclined hole of second channel 122.According to this structure, after pressure reduced, refrigeration agent flow through the bottom of slide opening 124, and the low pressure of pressure after reducing with first to the 3rd embodiment in identical mode act on the operating stem 135.
(the 6th embodiment)
In the previous embodiment, transmission component 163, operating stem 135 and valve body 130 form the element that (separates) separately and are engaged with each other then or cooperate and be used for assembling, and still, they can be integrally formed.Particularly, operating stem 135 and transmission component 163 can form integral body as shown in Figure 9.
(the 7th embodiment)
Previous embodiment is used operating stem 135 to be coupled in the end in the end of valve body 130 to be used for the structure that assembled construction or operating stem 135 and valve body 30 form as one.Yet structure is not defined in this especially, can use the regulatory function of being undertaken by engagement to change the length of operating stem 135 yet.
Particularly, the end patchhole 130a that has with nut portion 135a is formed on a tail end in the end of guided portion 132 of valve body 130, and is formed on as shown in Figure 12 in the operating stem 135 with the nut portion 135a of patchhole 130a engagement.
When valve body 130 was assembled on the valve chest 110, an end in the end of operating stem 135 was screwed in the patchhole 130a of guided portion 132 in advance.Under the situation of the periphery that is placed into valve element 131, spring element 133 inserts from the opening end of slide opening 124.So, spring element 133 and valve body 130 can be received in the slide opening 124 from a direction.
Admit surperficially 128 the time when seal element 167 is assembled to, another end of operating stem 135 is assembled in the transmission component 163 and displacement component 160 is engaged, thereby displacement component 160 can be set on the valve chest 110.
Secondly, operating stem 135 rotates to change its depth of engagement from the left and right sides open part of third channel 123.Thereby the length of operating stem 135 can be conditioned.In other words,, can realize the degree of superheat, comprise the spring force of spring element 133 by regulating the length of operating stem 135, meticulous adjusting.
At this moment, by form by quill shaft operating stem 135 and in the drawings shown in the arrow on the direction ca(u)lk (or pounding the limit) can prevent to regulate the loosening of rear thread part to connect guided portion 132.Be not provided with under the situation of controlling mechanism independently, having this expansion of structure valve 1 can be easily and accurately regulate the degree of superheat.
In other words, under the situation that does not increase the number of components, can realize the accurate adjusting of the degree of superheat, and becoming flexible after can preventing to regulate.Guided portion 132 is coupled by ca(u)lk after the length adjustment, but also can use the fixative that is used for fixing mutual helical thread portion.
(the 8th embodiment)
Among above-mentioned the 7th embodiment, operating stem 135 and valve body 130 interconnect with the accurate adjusting degree of superheat by connection.Except this structure, also can be provided as the individual component of adjusting screw rod mechanism.
Particularly, the shape of valve body 130 and valve chest 110 forms the bottom that can be arranged on slide opening 124 as the adjusting screw rod element 140 of controlling mechanism as shown in Figure 13, and spring element 133 can be arranged between the lower end of this adjusting screw rod element 140 and valve body 130.The shape of adjusting screw rod element 140 forms thereon the surface and admits a end in the end of spring element 133.Groove forms the top in week outside and helical thread portion is formed on the bottom.The 4th seal element 139 such as O shape ring is arranged in the peripheral groove to cut off the bottom of slide opening 124 and being communicated with of outside.
And hex hole 141 is formed on the bottom of adjusting screw rod element 140, and screw element 140 is by using the helical thread portion that is screwed into slide opening 124 such as the instrument of spanner.The bottom that slide opening 124 forms in valve chest 110 has helical thread portion.
According to said structure, the elastic force of spring element 133 can bias voltage displacement component 160 by valve body 130 and operating stem 135, and can realize the meticulous adjusting of the degree of superheat by adjusting screw rod element 140.In this embodiment, adjusting screw rod element 140 is at first back-outed from open end side, and spring element 130 and valve element 131 are inserted into then.So, can realize from a direction assembling.
(other embodiments)
In the previous embodiment, spring element 133 is contained in the slide opening 124 with valve body 130, but this structure is not restrictive.That is, spring element 133 can be arranged in the open part 127 below the displacement component 160 as shown in Figure 14.
In other words, an end in the end of spring element 133 is arranged in the open part 127 that is formed in the valve chest 110, and another end is arranged in the lower end of transmission component 163.The spring force bias voltage of spring element 133 is to displacement component 160 as a result.In the case, needn't in valve body 130, form and have larger-diameter guided portion 132.Slide opening 124 and valve body 130 can form simple shape.
Although described when of the present invention with reference to the specific embodiment chosen for the purpose of illustration, be apparent that under the situation that does not depart from basic conception of the present invention and protection domain, those skilled in the art can do a lot of modifications to described embodiment.
Claims (13)
1, a kind of temperature-type expansion valve comprises:
Valve chest, described valve chest has that high-pressure refrigerant flows to first passage in it, the low pressure refrigerant that flows to vaporizer flows through its second channel, the refrigeration agent of described evaporator outlet side flows through its third channel, and the throttling passage that is communicated with described first passage and described second channel;
Valve body, described valve body have the valve element of the sectional area that changes described throttling passage;
Operating stem, described operating stem is used for driving described valve body in linkage with displacement component, and described displacement component produces displacement according to the pressure difference between the evaporating pressure of saturation pressure corresponding with the outlet temperature of the refrigeration agent that flows through described third channel and described vaporizer;
Wherein be formed in the described valve chest with the slide opening that described throttling passage is communicated with and holds described valve body; And
Described valve element and described operating stem move in described slide opening in linkage, thereby regulate the sectional area of described throttling passage.
2, temperature-type expansion valve according to claim 1, wherein conduct forms by this way from the described slide opening in the hole of a direction formation of described valve chest, be the tip engages that described valve body can be from the end of described slide opening, and near described throttling passage opening its bottom.
3, temperature-type expansion valve according to claim 1, wherein said valve body has valve element and guided portion, and described valve element has the bar-like shape of minor diameter, and described guided portion has the diameter bigger than described valve body.
4, temperature-type expansion valve according to claim 3, wherein the connecting port as fluid passage is formed in the described valve element, and at least one and described operating stem in the described connecting port opening area of regulating described throttling passage in linkage.
5, temperature-type expansion valve according to claim 4, at least one in the wherein said connecting port is towards the bottom opening of described slide opening.
6, temperature-type expansion valve according to claim 3 wherein forms as the peripheral groove of the fluid passage periphery around described valve element, and described peripheral groove and described operating stem are regulated the opening area of described throttling passage in linkage.
7, temperature-type expansion valve according to claim 4, wherein said throttling passage has such sectional shape, and the relation between the displacement amount of promptly described valve element and the opening area of throttling passage is proportional substantially.
8, temperature-type expansion valve according to claim 1, wherein said valve body comprise first seal element that is used for the pressure difference between described third channel of gas tight seal and the described second channel.
9, temperature-type expansion valve according to claim 1, wherein said valve body comprise second seal element that is used for the pressure difference between described first passage of gas tight seal and the described second channel.
10, temperature-type expansion valve according to claim 1, also comprise the spring element that is used to encourage described displacement component and be used to regulate the adjusting screw rod element of the spring force of described spring element, the outlet refrigeration agent that described spring element is arranged as described vaporizer has the degree of superheat, and wherein said spring element places between described valve body and the described adjusting screw rod element.
11, temperature-type expansion valve according to claim 1, also comprise spring element, described spring element is used to encourage described displacement component, and the outlet refrigeration agent that described spring element is arranged as described vaporizer has the degree of superheat, and wherein said spring element places between described valve body and the described slide opening.
12, temperature-type expansion valve according to claim 11, wherein said valve body and described operating stem form the spring force that can regulate described spring element.
13, temperature-type expansion valve according to claim 1, wherein said displacement component has the transmission component that is used for driving force is delivered to described operating stem, and described valve body and described operating stem or comprise that the described transmission component of described operating stem is integrally formed.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005219353 | 2005-07-28 | ||
| JP2005-219353 | 2005-07-28 | ||
| JP2005219353A JP4706372B2 (en) | 2005-07-28 | 2005-07-28 | Thermal expansion valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1904420A true CN1904420A (en) | 2007-01-31 |
| CN100425930C CN100425930C (en) | 2008-10-15 |
Family
ID=37673735
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006101087065A Expired - Fee Related CN100425930C (en) | 2005-07-28 | 2006-07-28 | Temperature-type expansion valve |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US7624930B2 (en) |
| JP (1) | JP4706372B2 (en) |
| KR (1) | KR100794980B1 (en) |
| CN (1) | CN100425930C (en) |
| DE (1) | DE102006034813A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102759235A (en) * | 2011-04-27 | 2012-10-31 | 株式会社鹭宫制作所 | Thermostatic expansion valve |
| CN102759234A (en) * | 2011-04-27 | 2012-10-31 | 株式会社鹭宫制作所 | Thermostatic expansion valve |
| CN103889750A (en) * | 2011-08-25 | 2014-06-25 | 法雷奥热系统公司 | Device for controlling the flow of a coolant, and circuit including such a device |
| CN105579793A (en) * | 2013-09-11 | 2016-05-11 | 株式会社电装 | Expansion valve |
| CN107850224A (en) * | 2015-08-03 | 2018-03-27 | 株式会社电装 | Pile-up valve |
| CN110397758A (en) * | 2018-04-24 | 2019-11-01 | 盾安汽车热管理科技有限公司 | A kind of expansion valve and Gas-supplying enthalpy-increasing system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4868354B2 (en) * | 2006-02-27 | 2012-02-01 | 三洋電機株式会社 | Refrigeration cycle equipment |
| US20090145166A1 (en) * | 2007-12-06 | 2009-06-11 | Zheng Lou | Noise Reduction in a Thermostatic Expansion Valve |
| WO2009104238A1 (en) * | 2008-02-18 | 2009-08-27 | 株式会社鷺宮製作所 | Pressure type expansion valve |
| EP2565065B1 (en) * | 2010-04-26 | 2014-10-22 | Toyota Jidosha Kabushiki Kaisha | Air conditioning device for vehicle |
| CN102466377B (en) * | 2010-11-18 | 2014-10-29 | 浙江三花股份有限公司 | Expansion valve |
| CN102954634B (en) * | 2011-08-18 | 2015-05-06 | 苏州三星电子有限公司 | Thermostatic expansion valve |
| US9188375B2 (en) * | 2013-12-04 | 2015-11-17 | Zhejiang Dunan Hetian Metal Co., Ltd. | Control element and check valve assembly |
| US10431428B2 (en) | 2014-01-10 | 2019-10-01 | Reno Technologies, Inc. | System for providing variable capacitance |
| JP2016223751A (en) * | 2015-06-04 | 2016-12-28 | 株式会社テージーケー | Expansion valve |
| CN110486991B (en) * | 2019-09-09 | 2020-08-21 | 珠海格力电器股份有限公司 | Method, device and equipment for controlling step-out of electronic expansion valve and storage medium |
| CN113090659B (en) * | 2021-03-04 | 2022-03-29 | 湖南大学 | Bionic active static pressure gas bearing |
Family Cites Families (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3699778A (en) * | 1971-03-29 | 1972-10-24 | Controls Co Of America | Thermal expansion valve with rapid pressure equalizer |
| JPS55133177A (en) | 1979-04-04 | 1980-10-16 | Toshiba Corp | Memory communication system |
| JPS585163Y2 (en) * | 1980-04-25 | 1983-01-28 | 株式会社 鷲宮製作所 | Reversible electric expansion valve |
| JPH01225864A (en) * | 1988-03-04 | 1989-09-08 | Matsushita Refrig Co Ltd | Electric expansion valve control device for air-conditioning machine |
| JP2541659B2 (en) * | 1989-06-07 | 1996-10-09 | 株式会社 鷺宮製作所 | Temperature expansion valve |
| JPH0411366U (en) * | 1990-05-14 | 1992-01-30 | ||
| JPH04366376A (en) * | 1991-06-13 | 1992-12-18 | Nippondenso Co Ltd | Expansion valve |
| US5269459A (en) * | 1991-10-17 | 1993-12-14 | Eaton Corporation | Thermally responsive expansion valve |
| US5460349A (en) * | 1992-09-25 | 1995-10-24 | Parker-Hannifin Corporation | Expansion valve control element for air conditioning system |
| JPH08135841A (en) * | 1994-11-14 | 1996-05-31 | Nippondenso Co Ltd | Temperature type expansion valve |
| JPH08152232A (en) * | 1994-11-25 | 1996-06-11 | Zexel Corp | Expansion valve |
| JPH08291954A (en) | 1995-04-20 | 1996-11-05 | Nippondenso Co Ltd | Temperature type expansion valve |
| US5675982A (en) * | 1996-04-26 | 1997-10-14 | Rocky Research | Pulsed operation control valve |
| GB2317217A (en) * | 1996-09-04 | 1998-03-18 | Artform Int Ltd | Thermostatic radiator valve |
| US6062484A (en) * | 1998-05-20 | 2000-05-16 | Eaton Corporation | Modular thermal expansion valve and cartridge therefor |
| JP3820066B2 (en) * | 1999-10-15 | 2006-09-13 | 株式会社テージーケー | Expansion valve for refrigeration equipment |
| JP2002000031A (en) | 2000-06-27 | 2002-01-08 | Yanmar Agricult Equip Co Ltd | Mowing apparatus |
| JP4162839B2 (en) * | 2000-08-10 | 2008-10-08 | 株式会社不二工機 | Thermal expansion valve |
| JP2002054860A (en) * | 2000-08-10 | 2002-02-20 | Fuji Koki Corp | Thermostatic expansion valve |
| JP3815978B2 (en) * | 2001-04-13 | 2006-08-30 | 株式会社不二工機 | Thermal expansion valve |
-
2005
- 2005-07-28 JP JP2005219353A patent/JP4706372B2/en not_active Expired - Fee Related
-
2006
- 2006-07-25 US US11/492,560 patent/US7624930B2/en not_active Expired - Fee Related
- 2006-07-27 DE DE200610034813 patent/DE102006034813A1/en not_active Withdrawn
- 2006-07-28 KR KR1020060071557A patent/KR100794980B1/en not_active IP Right Cessation
- 2006-07-28 CN CNB2006101087065A patent/CN100425930C/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102759235A (en) * | 2011-04-27 | 2012-10-31 | 株式会社鹭宫制作所 | Thermostatic expansion valve |
| CN102759234A (en) * | 2011-04-27 | 2012-10-31 | 株式会社鹭宫制作所 | Thermostatic expansion valve |
| CN102759234B (en) * | 2011-04-27 | 2014-06-25 | 株式会社鹭宫制作所 | Thermostatic expansion valve |
| CN102759235B (en) * | 2011-04-27 | 2014-07-16 | 株式会社鹭宫制作所 | Thermostatic expansion valve |
| CN103889750A (en) * | 2011-08-25 | 2014-06-25 | 法雷奥热系统公司 | Device for controlling the flow of a coolant, and circuit including such a device |
| CN103889750B (en) * | 2011-08-25 | 2016-02-03 | 法雷奥热系统公司 | For device and the loop comprising such device of controlled cooling model agent stream |
| CN105579793A (en) * | 2013-09-11 | 2016-05-11 | 株式会社电装 | Expansion valve |
| CN107850224A (en) * | 2015-08-03 | 2018-03-27 | 株式会社电装 | Pile-up valve |
| CN110397758A (en) * | 2018-04-24 | 2019-11-01 | 盾安汽车热管理科技有限公司 | A kind of expansion valve and Gas-supplying enthalpy-increasing system |
| CN110397758B (en) * | 2018-04-24 | 2022-03-08 | 盾安汽车热管理科技有限公司 | Expansion valve and air-supplying enthalpy-increasing system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4706372B2 (en) | 2011-06-22 |
| KR100794980B1 (en) | 2008-01-16 |
| DE102006034813A1 (en) | 2007-04-05 |
| CN100425930C (en) | 2008-10-15 |
| JP2007032986A (en) | 2007-02-08 |
| US20070022769A1 (en) | 2007-02-01 |
| US7624930B2 (en) | 2009-12-01 |
| KR20070015088A (en) | 2007-02-01 |
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